Lubricant dispensing means and system

ABSTRACT

A means and method for dispensing a viscous fluid in metered amounts to provide lubricity for metal drawing in a forming press and which includes a positive displacement pump having an integral piston head and plunger construction, one-way ball check valves in inlet and outlet flow passages, spray nozzles connected to the pumps outlet ports by flexible conduit lines and swival mounted on magnetic mounting blocks for positioning ease, adjustment means on the pump for metering control by positioning an abutment stop within the piston chamber area, and a manually operated air valve for cyclic operation of the fluid pump in the normal operating use of the forming press.

iii-mite States Patent 1 Maddoclt [111 3,759,424 Sept. 18, 1973 LUBRICANT DISPENSING MEANS AND SYSTEM Primary Examiner-Samuel F. Coleman [76] lnventor: Edwin A. Maddock, 1510 Cherokee, Attorney-Dale wmme Royal Oak, Mich. 48067 22 Filed: Dec. 28,1970 [57] ABSTRACT A means and method for dispensing a viscous fluid in [211 App! 101380 metered amounts to provide lubricity for metal drawing in a forming press and which includes a positive dis- [52] US. Cl. 222/309, 222/334 placement pump having an integral piston head and [51] int. Cl. 60" 11/06 plunger construction, one-way ball check valves in inlet [58] Field of Search 222/129, 12, 309, and outlet flow passages, spray nozzles connected to 222/334, 250; 4 1 7/401 403, 571 the pumps outlet ports by flexible conduit lines and swival mounted on magnetic mounting blocks for position- [56] References Cited ing ease, adjustment means on the: pump for metering UNITED STATES PATENTS control by positioning an abutment stop within the pis- 2,532,679 12/1950 Slater 417 403 X chafnber and a mafluany P air valve 3,250,247 5 1966 Beaman 417 403 x for f 0Peratlon oftlle fluld P the "mmal P- 3,370,545 2/1968 Waibel 417/571 eratmg use of the formmgpress- 3,431,953 3/1969 Rutherford 222/334 X 3,497,111 2 1970 Savage 222/309 x 6 Clam, 8 Drawmg 7 52 12 5Q l l 1 l A EIZTMT-EI 2K y I}! v j .1 'l U. 22 I 76- J p.. w r '1 1 1 1 1 1| "3 1 83 I 1 1 8 g /5 k 116 \.p

k 1 "l' T 1 1 1 fil c444 LUBRICANT DISPENSING MEANS AND SYSTEM BACKGROUND OF THE INVENTION Sheet metal that is used in a stamping press, to form work parts, where there is any draw of the metal in the forming operation, usually requires some preparation ahead of time. That is, the sheet metal usually needs to be sprayed, coated or otherwise treated with some type of lubricating material at least in the critical areas of the draw where tears or ruptures in the material due to frictional forces inhibiting proper metal flow might otherwise occur. These areas include corners and confined spaces, in the dies, and where the draw is relatively deep for the gauge or thickness of the sheet material that is used.

Spraying a lubricant into the dies or on the sheet metal in the dies, at the stress areas, is usually preferred to dipping, coating or other spot treatment because less lubricating material is used. In I this regard, a solid stream or jet spray is better than an atomized spray since the latter involves overspray problems.

The better the directional control of the spray the less lubricating material that is required to do a job and the greater savings there is. This is true not only in the use of less lubricant but there is also a savings in the clean-up required afterwards.

The amount of lubricant required in any given situation depends on the lubricityneeded, which in turn depends on the surface tension of the work material, the frictional forces generated in the draw, etc. Nomore should be provided than can be used in the draw or draws to be performed, to. minimize or avoid cleanup problems afterwards. All these factors must be considered, but equally important is the system to meter and provide the precise amounts at the exact location where needed, irrespective of the viscosity of the lubricant, be it extremely light or heavy, or of the relative quantity or even different spot locations to be serviced. 1

Heretofore such systems have had to be tailored for each and every job, at considerable engineering and in-.

t stallation expense. No equipment has been available which would provide the capacity needed for a suffi ciently wide range of applications to enable its use for a number of different situations, quantity, or viscosity requirements. 1 A duplication of systems is not the answer, since it merely doubles costs. Greater viscosity of itself should not require largersized fluid lines, bigger nozzles,

larger chamber areas,.different fluid pumps. There is need for a jet spray system for metal forming operations and other uses'that previously just have not been available.

SUMMARY OF THE INVENTION The present invention is directed to a new and novel positive displacement pump and-a fluid supply system that is particularly designed to handle lubricating fluids for metal forming uses.

means and by quick response flow control check valves. 1

Flexible flow control lines and jet nozzles mounted for swivel positioning on magnetic blocks, enable ready positioning and changes as needed for the best possible directional control on a job.

Air valve operation of the pump assures positive response and control for each call for lubricating fluid made by a stamping press in the course of its metal forming operation.

These and othcr features of the present invention will be more fully described in the description of a preferred embodiment which follows.

DESCRIPTION OF THE DRAWING FIGURES FIG. 1 is a diagramatic layout of the different component parts of the spray system of the present invention.

FIGS. 2 and 3 are cross-sectional views through the fluid pump showing the positive displacement piston part in different operative positions in the different figures.

FIG. 4 is a crosssectional view taken from the preceding figure in the plane of line 4-4 therein and showing most of the fluid passages and passageways in the pump body. 1

FIG. 5 is a cross-sectional view of. the lower part of the pump body as seen in the plane of line 5-5 in FIG. 4, to showv adifferentview of certain of the fluid flow passages.

FIG.-6 is a side view of the pump, as seen in the plane of line 6-6 in FIG. 4, showing the air pressure inlet parts-and passages, principally.

FIG. 7 is a cross-sectional view of a fragmentary part of the pumpwith the air valve operating means shown diagramatically therewith. 7

FIG. 8 is a side elevation of a stamping press with the hydraulic spray system of the present invention installed for use thereon.

DESCRIPTION OF THE PREFERRED- EMBODIMENTS The hydraulic spray system of the present invention includes a reservoir tank 10 to which is connected the positive displacement pump 12, through a'filter 14. The pump 12 is controlled by a four-way air valve 16 and is shown connected to two separate spray nozzles 18 and'20, in the first drawing figure. I i

The tank 10. is made of a translucent plastic material,

so that the level of lubricant in it is always'visible. It is also made with reinforcing ribs 22 which serve both structurally and as sort of sight gauges to show the amount of lubricating fluid that remains in the tank. A cover'24 closes the top of the tank and enables the reservoir tank to be used as the shipping container for the whole system, with the shutoff valve 26 at the outlet port removed and stored with the fluid lines and other parts in the tank.

Polypropo'lene or other suitable plastic tubing is used for all of the fluid lines, in whatever lengths are required. A short piece 28 connects the shut-off valve 26 on the tank to he filter 14 and another piece 30 connects the filter to the pump 12. Air lines 32, 34 and 36 connect the air valve 16 to an air pressure supply source and the valve to the pump 12. And, fluid lines 38 and 40 are from the pump to the spray nozzles 18 and 20. V V

The positive displacement pump 12 is an important part of the overall system. It'includes a body housing part 42 within which is provided a piston chamber area 44 that is closed by a cover part 46 which includes means for setting a stop that limits the stroke of the fluid dispensing piston in the pump.

The piston member in the pump includes an enlarged head end 48 fitted in the piston chamber area 44 and having suitable rings 52 and seals 54 to make it hold a good seal and be responsive to air pressure on opposite sides. The innermost end 56 of the piston member is smaller and made to fit through a sealing ring 58 held in the lower end of the chamber area 44 by a snap ring 60 in a receptive snap ring groove 62. It has fluid seals 64, through which the plunger end 56 of the piston extends, and its own O-ring seal 66 next to the chamber wall.

The sealing ring 58 is also formed to provide an annular space 68 between itself and the chamber wall which registers with an air passage 70 in the housing wall.

There is, in turn, a passage 72 through it that communicates with the underside of the piston head 48.

The innermost end of the chamber space 44 is formed to provide a smaller area 74 within which the smaller end 56 of the pump piston is more closely received. There is, however, clearance space between the two to allow fluid flow between them, as best shown in FIG, 3.

A blind passage 76 is formed under the retainer ring 58 on one side of the pump space 74 and another, identified as 78, is formed across from it, on the other side. These are the inlet and outlet passageways, respectively, that connect to the pump space 74 and each has a one-way ball check valve 80 and 82 in it for the intended directional flow. A light spring 84 holds the check valve ball 80 down on a seat 86 formed in the passageway 76 while a spring 88 in the other passageway 78 holds its check valve ball 82 up against a seating ring 90. The seating ring has an -ring seal 92 around it, to prevent any by-pass fluid flow, and it is spaced apart from the retainer ring 58 by spacer parts 94 that areformed on it to allow fluid flow around and through it.

FIG. 4 shows the inlet passage 96 that the filter line 30-is connected to in providing fluid through ball check valve 80 to the pump 12. It also shows the passageway 98 that connects to the outlet manifold passage 100 from which there are five separate outlet ports; identi fied 101, 102, 103, 104, 105. In the first figure, only outlet parts 102 and 104 are in use, with supply lines 38 and 40 which connect to the two spray nozzles used in this particular embodiment.

Also shown in this drawing figure is the air inlet passage 70 that connects with the air inlet port 106 which has the air line 36 from the four-way valve connected, in turn, to it. A second air control passage 108 is provided in the housing body 42 between an inlet port 110 and the upper end thereof, just under the cover part 46 and inside of the air seal gasket 112, so that it supplies air to the other side of the piston head 48.

The cover member 46 for the pump housing 42 is fastened to it by four recessed socket head screws, one in each corner, not shown. It has a center opening 114 which is threaded and it has an adjustable stop 116 in it with head end 118 recessed into the cover part over the piston head 48, when fully withdrawn. It also serves to restrict the stroke of the piston, and hence the amount of fluid that will be moved by the pump, when turned down into the chamber area 44.

An O-ring seal 120 around the stop end 118 prevents blow-by and assures against pressure loss at the cover end.

A knob 122 is fastened to the threaded post 116 of the stop, by a screw 124, and includes set screw 126 in its side wall flange, to hold and fix it in position (and hence the stop) in initially setting the pump requirements to specifications.

The four way valve connections to work the pump 12, are shown diagramatically in FIG. 7. v

The air valve 16, when energized, allows air flow through passage connections 128 and 130 to the flow lines 36 and 34 (reference FIG. 1) which connect to the passages and ports on opposite sides of the piston head 48. When the air valve is de-energized, the passage connections 132 and 134 in the valve connect to the flow lines 36 and 34 and the flow is in reverse, which retracts the piston and moves it toward its cover closure 46.

The air valve 16 is operated, to accomplish the change from direct to cross flow, by means of a control 136 which has a rod 138 set through one side of it and which serves to operate it when the rod contacts, or is contacted, by something.

FIG. 8 shows thesystem as installed for use on a stamping press 130.

The ram 132 is raised above the bed plate or platen 134 and shows the die form 136 over the reverse image die mold 138. The reservoir tank 10 is mounted on one side of the press, as is the filter 14, while the pump 12 and air valve 16 are disposed on part of the press frame 140 relatively over the ram 132.

When the ram is raised, as shown, it contacts (or includes means for contacting) the lever rod 138 on the air valve 14 which energizes the valve and allows air flow through flow line 34- into the pump 12. The air flow is via port 110 and passage 108 to over the piston 48, as shown in FIG. 7. Piston plunger part 56 pushes fluid from the smaller chamber space 74 through check valve 82, passage 98 and into the outlet manifold passage from which it passes into the two operative outlets 102 and 104. These are connected by flexible flow lines 38 and 40 to the spray nozzles 18 and 20.

The spray nozzles 18 and 20 are mounted in swival block supports on magnetic stay blocks and 200 which enables them to be positioned where and as desired and to be moved and changed as necessary to obtain the very best spray distribution pattern possible.

When the stamping press ram begins its descent, the lever rod 138 is released and the air valve control 136 (under internal spring load) returns the valve to its deenergized position which connects the air pressure line to the pump line 36 and, in turn, via passages 70 and 72 to the underside of piston head 48. This draws the piston plunger 56 out of the pump space 74, allows fluid pressure to unseat the ball check valve 80, and fluid to flow into and refill the pump space 74.

As will be appreciated, the fluid line pressure, for the lubricating spray fluid, is not enough to unseat the check valve ball 82, against the spring load holding it closed. It is only when the piston plunger 56 begins its descent and increases the unit pressure that the outlet ball check is popped open.

The piston member 48 in the pump is moved back towards the cover end 46 until it is stopped against the cover or the stop 118 if the latter is set-out therebelow. The travel of the piston determines the amount of fluid the pump will move and so setting the stop 118 down into the chamber area space 44 to limit its stroke will accomplish this objective. Actually, once the number of spray nozzles is determined, what their fluid requirements will be, viscosity of the fluid is known, etc., the stop 1W is set by the knob 1122 and its position is fixed by the set-screw 126. Its position is adjusted only in recalibrating the pump for the requirements of the system it serves,

I claim:

1. Apparatus for dispensing a viscous fluid in metered amounts and comprising; a one piece housing member having two contiginous chamber area spaces of respectively larger and smaller diametric size formed therewithin and from one end thereof, inlet and outlet passage means for viscous fluid formed in communication with said smaller chamber area space and having inlet and outlet check valves disposed respectively within the inner ends thereof, an intermediate member received and retained within said larger chamber area space and forming an end wall for both of said chamber area spaces and an abutment wall retentive of said check valves in said inlet and outlet passage means, passage means provided at opposite ends of said larger chamber area space for selective alternate communication with an air pressure supply source and an atmospheric vent, a differential piston member having its larger end received and guided within said larger chamber area space and its smaller end received and guided through said intermediate member and into said smaller chamber area space for inducing fluid flow thereinto and therefrom, and a cover member for closing the open end of said housing and having adjustable means provided therethrough and into said larger chamber area space for limiting the travel of the larger end of said differential piston member and thereby the volumetric induction and displacement of fluid by its smaller end within said smaller chamber area space.

2. The apparatus of claim ll, including chamber wall sealing means and sealing means receptive of the smaller end of said differential piston therethrough provided on and within said intermediate member for precluding air and fluid leakage between said chamber area spaces, and means received within said larger chamber area space and engaging the chamber wall thereof for retaining said intermediate member in relatively fixed relation therewithin.

3. The apparatus of claim 1, the passage means for air pressure supply and venting at the inner end of said larger chamber area space being provided at said intermediate member, said intermediate member having an annular space in communication with said passage means, and passage means provided in said intermediate member between said annular space and said larger chamber area space for communication therebetween.

4. The apparatus of claim 1, including an annular space of intermediate size formed within said housing between said larger and smaller chamber area spaces for providing a locating shoulder for said intermediate member, said check valves being disposed within the end wall of said annular space in abutting and retained Y engagement with said intermediate member, and said annular space providing open communication between said check valves and said smaller chamber area space.

5. The apparatus of claim 1, said housing member being rectilinear in shape and having a manifold passage formed wholly therewithin adjacent and normal to said smaller chamber are space, and said outlet passage means beingconnected to said manifold passage for providing multiple outlet connections therewith.

6. The apparatus of claim 1, including an annular space of intermediate size formed within said housing between said larger and smaller chamber area spaces for providing a locating shoulder for said intermediate member, said check valves being disposed within the end wall of said annular space in abutting and retained engagement with said intermediate member, and said annular space providing open communication between said check valves and said'sm'aller chamber area space, an annular space provided within said intermediate member and for open communication with the air pressure supply and venting passage means at the inner end of said larger chamber area space, passage means within said intermediate member between said annular space and said larger chamber area space for communication therebetween, sealing means on and within said intermediate member for precluding air and fluid leakage between said chamber area spaces, means received within said largerchamber area space and engaging the chamber wall thereof for relatively fixing the location of said intermediate member, and a manifold passage provided wholly within said housing member and in communication with said outlet passage means for pro- 

1. Apparatus for dispensing a viscous fluid in metered amounts and comprising; a one piece housing member having two contiginous chamber area spaces of respectively larger and smaller diametric size formed therewithin and from one end thereof, inlet and outlet passage means for viscous fluid formed in communication with said smaller chamber area space and having inlet and outlet check valves disposed respectively within the inner ends thereof, an intermediate member received and retained within said larger chamber area space and forming an end wall for both of said chamber area spaces and an abutment wall retentive of said check valves in said inlet and outlet passage means, passage means provided at opposite ends of said larger chamber area space for selective alternate communication with an air pressure supply source and an atmospheric vent, a differential piston member having its larger end received and guided within said larger chamber area space and its smaller end received and guided through said intermediate member and into said smaller chamber area space for inducing fluid flow thereinto and therefrom, and a cover member for closing the open end of said housing and having adjustable meanS provided therethrough and into said larger chamber area space for limiting the travel of the larger end of said differential piston member and thereby the volumetric induction and displacement of fluid by its smaller end within said smaller chamber area space.
 2. The apparatus of claim 1, including chamber wall sealing means and sealing means receptive of the smaller end of said differential piston therethrough provided on and within said intermediate member for precluding air and fluid leakage between said chamber area spaces, and means received within said larger chamber area space and engaging the chamber wall thereof for retaining said intermediate member in relatively fixed relation therewithin.
 3. The apparatus of claim 1, the passage means for air pressure supply and venting at the inner end of said larger chamber area space being provided at said intermediate member, said intermediate member having an annular space in communication with said passage means, and passage means provided in said intermediate member between said annular space and said larger chamber area space for communication therebetween.
 4. The apparatus of claim 1, including an annular space of intermediate size formed within said housing between said larger and smaller chamber area spaces for providing a locating shoulder for said intermediate member, said check valves being disposed within the end wall of said annular space in abutting and retained engagement with said intermediate member, and said annular space providing open communication between said check valves and said smaller chamber area space.
 5. The apparatus of claim 1, said housing member being rectilinear in shape and having a manifold passage formed wholly therewithin adjacent and normal to said smaller chamber are space, and said outlet passage means being connected to said manifold passage for providing multiple outlet connections therewith.
 6. The apparatus of claim 1, including an annular space of intermediate size formed within said housing between said larger and smaller chamber area spaces for providing a locating shoulder for said intermediate member, said check valves being disposed within the end wall of said annular space in abutting and retained engagement with said intermediate member, and said annular space providing open communication between said check valves and said smaller chamber area space, an annular space provided within said intermediate member and for open communication with the air pressure supply and venting passage means at the inner end of said larger chamber area space, passage means within said intermediate member between said annular space and said larger chamber area space for communication therebetween, sealing means on and within said intermediate member for precluding air and fluid leakage between said chamber area spaces, means received within said larger chamber area space and engaging the chamber wall thereof for relatively fixing the location of said intermediate member, and a manifold passage provided wholly within said housing member and in communication with said outlet passage means for providing multiple outlet connections therewith. 